Rotary engine

ABSTRACT

A rotary engine for use as a fluid pump or motor, gas compressor or vacuum pump, or internal combustion engine with improved performance and reduced exhaust emissions as compared to conventional engines. The rotary engine provides a cycle of alternately expanding and contracting volumes through purely rotational movement in certain embodiments, or through precessional-type movement in other embodiments. In one embodiment a stator element is formed with side walls which define an annular cavity through which primary and secondary rotors are adapted to turn with conjoint angular velocites about intersecting axes disposed at a predetermined oblique angular relationship. One or more vanes project into the cavity and are slidably fitted in cylindrical seals which accommodate relative swivel motion between the vanes and rotors throughout a full cycle of rotation. Inlet means is provided to direct the working fluid or a combustible charge into selected portions of two diametrically and axially opposed chambers, and outlet means is provided to direct the fluid or exhaust gasses from the chambers. In the internal combustion engine embodiment valve means is provided adjacent one vane to direct a compressed charge from the trailing portion of one chamber across to the leading portion of an opposite chamber where combustion occurs. In another embodiment a disc is mounted for precessional-type movement within a stator carrying one or more fixed vanes, with a power shaft rotatably mounted relative to the stator about a first axis, and with this shaft rotatably mounted relative to the disc about a second axis obliquely intersecting the first axis.

1 11 3,769,944 145 Nov. 6, 1973 ROTARY ENGINE [75] Inventor: Charles Raymond, Berkeley, Calif.

[73] Assigneez- Redskin Engines Company,

Berkeley, Calif.

22 med; May 8, 1972 21 Appl.No.:25 0,884

Related U.S. Application Data [63] Continuation-in-part of Ser. No. 197,449, Nov. 10,

1971, abandoned.

418/138, 418/193, 418/195- [51] Int. Cl F02b 53/06, FOlc 1/08, F03c 3/00 [58] Field of Search 123/823, 8.35, 8.41; I

[56] References Cited' UNITED STATES PATENTS 174,373 3/1876 Maxson 418/195 763,982 7/1904 Jahn, Jr. 418/1 93 2,101,051 12/1937 Cuny 418/195 X 2,101,428 12/1937 Cuny 418/195 X 2,691,349 10/1954 Cuny 418/219 X. 3,101,700 8/1963 Bowdish 418/193 X Primary Examiner-Allan D. Herrmann Att0rneyPaul D. Flehr et a1.

57 ABSTRACT A rotary engine for use as a fluid pump or motor, gas

compressor or vacuum pump, or internal combustion engine with improved performance and reduced exhaust emissions as compared to conventional engines. The rotary engine provides a cycleof alternately expanding and contracting volumes through purely rotational movement in certain embodiments, or through precessional-type movement in other embodiments. 1n one embodiment a stator element is formed with side walls which define an annular cavity through which primary and secondary rotors are adapted to turn with conjoint angular velocites about intersecting axes disposed at a predetermined oblique angular relationship. One or more vanes project into the cavity and are slidably fitted in cylindrical seals which accommodate relative swivel motion between the vanes and rotors throughout a full cycle of rotation. Inlet means is pro- 1 vided to direct the working fluid or a combustible charge into selected portions of two diametrically and axially opposed chambers, and outlet means is provided to direct the fluidor exhaust gasses from the 1 chambers. -In the internal combustion engine embodiment valve means is provided adjacent one vane to direct a compressed charge from the trailing portion of I one chamber. across to the leading portion of an opposite chamber where combustion occurs. lnanother embodiment a disc is mounted for precessional-type movement within a stator carrying one or more fixed vanes, with a power shaft rotatably mounted relative to the stator about a first axis, and with th'is shaft rotatably mounted relative to the disc-about a second axis obliquely intersecting the first axis;

48 Claims, 29 Drawing Figures PAIENI [Ham 5 I973 lOZ PAT-ENIEUimY 5197a 3.7691944 SIEU DZUF 12 PATENIEDrmv SISIS 3789.944

saw 030? 12 PATENIEUMBV BIBTS Y saw near 12 PATENTEU xuv 6 I975 sum 09M 12 I f I 7 5 ROTARY ENGINE CROSS-REFERENCE TORELATED APPLICATION This is a continuation-in-part of application Ser. No. 197,449 filed Nov. 10, 1971, and now abandoned.

BACKGROUND OF THE INVENTION This invention relates in general to rotary'engines, and in particular relates to improvements in rotary engines adapted for use as a fluid pump or motor, gas compressor or vacuum pump, or internal combustion engine. Y

There has been an increasing recog'nitionyof the disadvantages and limitations of conventional reciprocating piston engines, especially when viewed in comparison to rotary engines. It is recognized that reciprocating piston engines are relatively inefficient, have relatively unfavorable power-to-weight and torque characteristics, require the burningof relatively high octane fuels, emit a considerable amount of harmful exhaust pollutants, and have a relatively short life in view of vibration, wear and lubrication problems.

A number of rotary engine designs have been proposed in an attempt to solve the problems inherent in conventional reciprocating piston engines. Considerable activity has developed recently in this field for the internal combustion formof these rotary engines as a result of the serious air pollution resulting from conventional piston engines. Various forms of rotary en-. gines have developed to duplicate the usual intake compression-power-exhaust cycle. Among these prior art rotary engines are the eccentric rotor engines, such as the Wankel engine in which a rotor moves about a fixed gear within a trochoidai stator and with power delivered through an eccentric drive. Other types of rotary engines include those known as cat-and-mouse engines in which pistons travel in a circular path, multiple rotor engines employing two intermeshing rotors which turn about parallel axes, and revolving block engines which combine, reciprocating piston motion with rotational motion'of the engine block. However, each of the foregoing rotary engine designs have certain drawbacks or limitations. For exampleythe eccentric rotor engines present problems in cooling the elements and in -sealing the engine chambers. The need has therefore been recognized for an improved rotary engine of simplified design which eliminates or reduces the many in herent problems of existing'engines of both reciprocating piston and rotary engine design, which is adapted for many difierent types of commercial applications, and which will substantially reduce harmful exhaust emissions for internal combustion engine applications.

OBJECTS AND SUMMARY OF THE INVENTION It is a general object of the invention to provide an improved rotary engine adapted for use in different embodiments as a fluid pump/motor, gas compressor or vacuum pump, or internal combustion engine.

Another object is to provide an improved rotary en gine of the character described in which first and second rotor elements are mounted for rotation about angularly disposed; intersecting axis within a cavity formed in a stator and with a vane or vanes carried on one of the rotor elements so that conjoint rotation of the rotor elements relative to the stator causes the volumes defined in opposed chambe to alternately "ex character described for use in internal combustion cycling in which valve means is provided to control the flow of the compressed charge between chambers and is actuated in different embodiments responsive to the relative position assumed bythe stator and rotor elements as they rotate throughout a complete cycle.

Another object is toprovide a rotary engine of the character described {which includes means for effectively sealing the engines working chambers.

The foregoing and additional objects and features of the invention areprovided by stator and rotor elements arranged either to achieve purelyrotary motion in certain embodiments, or precessional-type motion in other embodiments. In the embodiment having purely rotary motion two rotor elements are mountedifor conjoint rotation about axes which intersect at a predetermined oblique angular relationship. In one embodiment an outer rotor carries at least one vane which projects into a stator cavity to define expanding and contracting volumes within diametrically opposed chambers. In another embodiment the outer rotor itself defines the chamber walls. Means is provided to form a swivel connection and seal between the vane and inner rotor to accommodate relative movement throughout rotation of the elements. Inlet and outlet means are provided to admit and discharge fluid into respective expanding and contracting volumes of the two chambers for the fluid pump/motor or gas compressor and vacuum pump embodiments. In the internal combustion embodiments inlet means is provided to direct a charge into the expanding volume of one chamber for the intake phase, valve means is provided to direct the compressed charge from the contracting volume of the first chamber following the compression phase to the expanding volume of the opposite chamber, ignition means then ignites the compressed and transferred charge for the power phase, and outlet means exhausts the spent gasses from the contracting volume of the opposite chamber for the exhaust phase. The valve means comprises in several embodiments either a one-way flow valve, or a positive action valve opening and closing responsive to the relative positions assumed between the stator and rotor elements throughout a complete cycle. A power shaft is connected in different embodiments to either of the rotor elements, or power maybe delivered through a suitable connection with the outer rotating surface of the outer rotor, as by a belt drive.

The embodiment of the invention which achieves purely rotary motion of the elements (acting as a positive displacement turbine affords important advantages over existing designs. For example, friction losses are lower, vibration is reduced, sealing is simplified,

plastic or metal seals having low friction and improved sealing properties. Thus, the moving surfaces may be lubricated without the introduction of the lubricant into the firing chamber, which otherwise would cause pollution. Depending upon the design parameters such as the oblique angular relationship between the rotor axes the volumes within the chambers can be varied over a range for a given size engine. In addition, a wide range of compression ratios is available depending upon the design parameters. The internal combustion engine embodiment provides an improved power-toweight ratio and favorable torque characteristics as compared to conventional engines. Primarily because of the absence of reciprocating parts the torque curve does not have the upper RPM limit bounded by an exponential friction curve as in conventional engines, allowing this rotary engine to run at extremely high speeds with minimal leakage or sealing losses. A highly important advantage to the invention lies in the substantial reduction in the emission of harmful exhaust pollutants, since both the mechanical and thermal efficiencies are much higher as a result of factors which include lower friction, longer power stroke than the intake-compression stroke, less heat loss to the engine, more homogeneous temperature distribution in the combustion zone allowing less surface-held unburned hydrocarbons, less requirement for leaded fuels, and the combustion forces act directly on the rotating members in the torque direction.

In the embodiment of the invention characterized in employing precessional-type motion a stator forms a cavity and carries one .or more inwardly projecting vanes. A disc is mounted for precessional-type motion within the cavity to define expanding and contracting volumes, with swivel seal means provided between the vane and disc. A power input/output shaft is rotatably mounted within the stator about a first axis, and the shaft is rotatably mounted relative to the disc about a second axis obliquely intersecting the first axis. Fluid inlet and outlet means are provided, and for gas compressor applications check valve means is provided to control gas flow.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. I is a cut-away perspective view of a rotary fluid engine embodiment of the invention;

FIG. 2 is an enlarged axial sectional view of the rotary engine of FIG. I; 7

FIG. 3 is a crosssectional view taken along the line 3-3 of FIG. 2;

FIG. 4 is a fragmentary sectional view taken along the line 4-4 of FIG. 2;

FIG. 5 is a schematic developmental view for the rotary engine of FIGS. l-4 illustrating the interrelationship of the elements creating expanding and contracting volumes within the engine;

FIG. 6 is a fragmentary cross-sectional view of an embodiment providing removable, radially adjustable vanes;

' FIG. 7 is a fragmentary cut-away sectional view of another embodiment of the engine of FIG. 1 illustrating details of a fluid valving arrangement;

FIG. 8 is a fragmentary cross sectional view of another embodiment of the engine of FIG. 1 illustrating details of another fluid valving arrangement;

FIG. 9 is an axial cross sectional view of an embodiment of the invention in which a through shaft turns with the primary rotor;

FIG. 10 is a schematic developmental view of an internal combustion engine embodiment of the invention;

FIG. 11 is a fragmentary axial sectional view of another embodiment of the invention illustrating details of a valving arrangement;

FIG. 12 is a developmental sectional view taken along the line 12-12 of FIG. 11;

FIG. 13 is a fragmentary developmental view of another embodiment of the invention illustrating details of a valving arrangement;

FIG. 14 is a fragmentary axial sectional view taken along the line 14-14 of FIG. 13;

FIG. 15 is a fragmentary axial sectional view of another embodiment of the invention illustrating details of a valving arrangement;

FIG. 16 is a developmental sectional along the line 16-16 of FIG. 15;

FIG. 17 is a fragmentary axial sectional view of another embodiment of the invention illustrating details of a valving arrangement;

FIG. 18 is a developmental sectional view taken along the line 18-18 of FIG. 17;

FIG. 19 is an axial sectional view of an embodiment in which an outer rotor defines the chamber walls and carries an inwardly projecting fixed vane;

FIG. 20 is a cross-sectional view taken along the line 20-20 of FIG. 19;

FIG. 21 is a fragmentary cross-sectional view of the vane and swivel seal taken along the line 21-21 of FIG. 19;-

FIG. 21a is a fragmentary cross-sectional view of an embodiment employing means for relieving pressure forces on the vane and swivel seal;

FIG. 22 is a developmental view partially in section taken along the line 22-22 of FIG. 19;

FIG. 23 is a fragmentary sectional view of an embodiment providing a chamber sealing arrangement for an engine of the type shown in FIG. 19;

FIG. 24 is a sectional view taken along the line 24-24 of FIG. 23;

FIG. 25 is a fragmentary sectional view of an embodiment providing another chamber sealing arrangement;

FIG. 26 is a fragmentary sectional view of an embodiment providing an additional chamber sealing arrangement;

FIG. 27 is an axial sectional view of an embodiment employing processional-type motion; and

FIG. 28 is a developmental view partially in section of an embodiment similar to that of FIG. 27 but employing a two vane construction.

DESCRIPTION OF THE PREFERRED EMBODIMENTS In the drawings FIG. 1 illustrates a rotary engine 20 of the invention comprising an embodiment adapted for use as a fluid pump/motor, gas compressor, or vacuum pump. Engine 20 includes three principal elements comprising a first element or stator 22,.a second element or secondary ring rotor 24, and a third element or primary rotor 26. The two rotor elements 24, 26 are mounted for conjoint rotation with respect to the fixed stator 22, which is anchored to a suitable base support 28. While this embodiment will be described in terms view taken of such a fixed stator carrying the moving rotors, it is understood that the invention also encompasses a rota'ry engine of the described nature in which the second element is anchored to a base support with the first element adapted to undergo rotary movement, or in which all three elements are adapted to move on a free turning mount for counter rotation.

As best illustrated in FIG. 2 stator 22 extends outwardly from the fixed base 28 to provide end-wise support for the remaining engine elements. The stator is formed with an annular cavity defined between internal side walls 30,32 extending radially outwardly from a flattened annular cavity 34 and axle portion 36.

Secondary rotor element 24 is formed'into an openended shell structure mounted on the stator by suitable ball bearing assemblies 38, 40 for rotation about a first axis 42. A power input/output shaft 44 is mounted on the closed end of the secondary rotor concentric with axis 42. The secondary rotor carries partition means comprising a pair of diametrically opposed 'vanes 46, 48 which are mounted to the inner surface 50 of this rotor and project radially inwardly into the stator cavity. While a pair of vanes are illustrated, it will be understood that the inventlon contemplates the number of vanes could be, greater than two with equal circumferentialspacing, or only one vane could be provided, depending upon the desired number of volumes around the'rotor. Innersurface 50 of the secondary rotor de:

fines a truncated section of a spherical surface to accept the relative lateral sliding motion of primary rotor 26.

Primary rotor 26 includes an inner hub 52 and integral radially extending disc portion 54. I-Iub 52 is mounted by means of ball bearing assemblies 56, 58 on stator axle 3,6 for rotation about a second axis 60 which intersects the first axis 42 at a predetermined oblique angle A so that'the two rotor elements turnin separate intersecting planes at the same angular velocity with respect-to the stator. The output surface 61 of the disc portion defines a truncated section of a spherical surface to interfit in close-spaced relationship with thefac' ing spherical surface 50 of rotor 24. A pair of suitable annular labyrinth type seals 62, 64 are provided be tween the stator'end edges and the inner facing portions of the secondary rotor for sealing the statorcavity against fluid or gas leakage.

The angular disposition of primary rotor disc portion 54 within the cavity of the stator divides the same into two diametrically and axially opposed chambers 66, 68 (FIG. 1). The two chambers remain fixed in positional relationship with respect to the stator element, and the conjoint movement of the two rotor elements carrying the vanes through the chamber creates the expanding and contracting volumes therein in a manner to be presently described. The stator side walls 30, 32 are formed with respective diametrically opposed flat surfaces 70, 72 each defining annular sectors positioned in close-spaced relationship with the opposed rotating flat surface of a respective side of rotor disc 54. The remaining portions of the stator side walls are formed into diametrically opposed surfaces 74, 76 each defining truncated segments of a conical surface. The conical surface portions of the stator side walls'provide close-spaced relative motion with respect to the radial edges of vanes 46, 48 moving through the chambers.

It is thus seen that the enclosed volumes of the two chambers are defined between the inner surface 50 of the second rotor element, the facing sector of the side surface of third element disc portion 54, and either of the stator conical surfaces 74, 76. Successive movement of the vanes 46, 48 as they are carried through the chambers causes the volumes defined in each chamber in front of vane movement to contract, while the volumes defined behind vane movement expand.

As the two rotor elements turn relative to the stator about their axes 42, 60, the vanes 46, 48 undergo a swivel movement relative to second element 24 about radially extending axes. Swivel seal means 78, 80 provide a swivel connection between the vanes and second and third elements to accommodate this relative swivel movement and at the same time provide a fluid-tight seal for containing the fluid or gasses within the chambers. The swivel seal means comprise cylinders 82, 84 seated within respective radially extending diametrically opposed bores 86, 88 formed in third rotor element disc portion 54.

As bestillustrated in FIG. '4, the typical cylinder 82 is provided with a lateral slot 90 adapted to slidably receive the corresponding vaner48, and the rotor disc portion 54 is provided with enlarged slots 92 to accept the arc of swivel movement of the corresponding vane. It will be seen that as the two rotor elements turn throughout a complete cycle each vane undergoes two distinct movementspThe first movement comprises a lateral sliding movement of the vane through the cylinder slot from, for example, the extreme lateral position with the vane midway through the chamber 68, as illustrated in FIG. 2, across through the slot to the extreme opposite position with the vane moved to a position midway through the opposite chamber 66, and then back to the first mentioned extreme position at the completion of the cycle. At the same time the relative movement of the two rotor elements 24, 26 causes the vane 48 and swivel cylinder 82 to pivot or swivel about a radial axis relative to disc portion 54 of the third element. This swivel action progresses from the perpendicular relationship between vane and rotor disc of FIG. 4 with the vane midway through chamber 68, through an angle B as the vane and rotor elements rotate through an angle of 90 relative to the stator, back to the perpendicular vane position through the next quadrant of rotation with the vane disposed midway throughthe opposite chamber 66, through an angle B as the vane and rotor elements turn through the next quadrant, and then back to the normal perpendicular vane position through the final quadrant of rotation for completion of the cycle.

The vane edges are sealed with respect to the stator side walls and third element hub 52 by means of suitable U-shaped seal elements 94, 96, which may be segmented, disposed in slots formed along each of the vane side edges and inwardly projecting edges; The radially straight portion of seals 94,96 are only in contact with the stator conical surfaces 74, 76 as a respective side of each vane moves through a chambenThe axial width of each vane is sized to be less than the corresponding width' of the stator cavity such that as each vane edge moves adjacent a facing flat stator surface 70 or 72it will retreat from this surface into the slot 90 of the swivel seal connection. It is seen that the effective sealing contact between the stator and third rotor element 26 is projected over the entirearea of flat surface 72. The wear on the seals 94, 96 is substantially reduced in that vane edge sealing contact occurs during only a part of vane travel through one complete cycle. The invention contemplates that vane width could substantially equal stator cavity width to provide continual vane edge sealing contact.

A pair of annular seals 98, 100 (FIG. 1) are provided to seal the outer spherical surface 61 of rotor disc portion 54 with respect to the inner spherical surface 50- of second rotor element 24. These seals may comprise segmented rings seated in annular grooves formed in the rotor disc portion. The segmented ring seals may be urged radially outwardly by suitable spring loading means into tight-fitting sealing relationship with the second rotor element. These seals are only required to undergo lateral sliding movement between the second and third rotor elements throughout a complete cycle of rotation and do not undergo high speed rotary contact inasmuch as the two rotors turn in conjoint angular relationship. Because the two vanes 46, 48 are secured to and project inwardly from the second rotor element 24 it is therefore not necessary to provide sealing means at the juncture of the vanes and second rotor element.

While the invention has been described in the embodiment of FIGS. I-5 wherein the vanes are fixed for rotation with second rotor element 24, it is understood that the invention contemplates that the vanes could be fixed with respect to the third rotor element 26 and with a swivel connection provided between the second rotor and outer portion or root of each vane permitting the vanes to undergo the swivel movement throughout a complete turning cycle. Where an engine of the invention is utilized to develop power by the forces of expanding fluids or gasses within the chambers, it will be appreciated that the embodiment of FIGS. 1-5 provides a driving torque acting against the vanes and which is carried directly through to the second rotor element 24 and drive shaft 44 without being transferred across a swivel connection. FIG. 9 illustrates. an embodiment in which the power output shaft is connected with the third rotor element which in turn is driven through the swivel seals by the fluid forces acting on vanes carried by the second rotor element.

It is to be noted that the relative swivel movement be tween the vanes and swivel seal connection with the third rotor element is purely a result of the geometry of the rotor elements as they turn through separate intersecting planes. There is no requirement for application of external forces, as by camming means, to turn the vanes through their swivel displacement.

The geometry of the elements of engine may be selectively varied to provide any desired ratio between the expanding and contracting volumes of the chambers depending upon particular specifications and requirements. Thus, for an engine of given size the volumes of the chambers may be varied by varying the ineluded angle A between the rotor axes 42, 60. An increase in the angle A will result in a corresponding increase in chamber volume for an engine of the same overall size and diameter.

FIGS. 2, 3 and 5 illustrate details of the inlet and outlet means to introduce and discharge fluid into the chambers. The inlets and outlets are described in relation to a clockwise rotation of the two rotor elements as viewed in FIG. 3, and it will be realized that a reversal of the sense of rotation will reverse the direction of fluid movement. It will be noted that in the developed view of FIG. 5 the edge of the stator and second rotor elements are shown as straight while, for clarity, the third rotor element edge is shown as curved. The inlet means includes a main inlet conduit 102 connected with a branched passage or conduit 104 formed in stator element 22. Conduit 104 has a branch 106 leading to a port 108 opening into the leading portion of chamber 66. The inlet means further includes a branch 110 extending through the center of stator axle 36 with a reverse channel leading to port 112 opening into the leading portion of chamber 68. The outlet means includes a main outlet conduit 114 connected with branched outlet passage or conduit 116 formed in the stator. Conduit 116 includes a branch 118 opening into a port 124 in the trailing portion of chamber 66, and a branch 120 which extends through the stator axle 36 with a reverse channel leading to port 122 opening into the trailing portion of chamber 68.

The operation of the embodiment of FIGS. I-5 is best illustrated in the developmental view of FIG. 5. The rotary engine 20 is used to provide a source of pressurized fluid, for example as a pump or gas compressor,by connecting the inlet conduit 10?. with the source of fluid, such as an oil reservoir, and the outlet conduit 1 14 with the desired fluid system to be pressurized. Power from a suitable source isapplied to shaft 44 for turning the primary and secondary rotor elements in a rotational sense from top to bottom as viewed in FIG. 5. As the diametrically opposed vanes 48, 46 sweep by the inlet ports 108, 112 and extend outwardly from the swivel seals, the volumes defined in the leading portions of the chambers 66, 68 expand so that fluid is inducted from the branch passages leading from inlet conduit 102. This proceeds so that a maximum volume of fluid is drawn into the two chambers, and continued revolution of the rotor elements then moves the vanes over the discharge ports 122, 124. The fluid is discharged under pressure from the chambers as the vanes trailing the fluid charge progressively advance in relation to the stator behind the inducted charge. The resulting contraction of the volumes of the trailing portions of chamber 66, 68 forces the fluid through the discharge ports exposed by the vanes and through discharge conduit 114. It will be seen that each of the two vanes act to push fluid ahead of the leading vane surface for the pressure phase while at the same time drawing in fluid behind the trailing vane surface for the suction phase. Reversal of the sense of rotation of the rotor elements affords automatic reversal of the inlet and outlet fluid flows. That is, conduit 114 becomes the suction inlet while conduit 102 becomes the pressure outlet.

The intake/exhaust porting arrangement may be widely varied for different applications. It is preferred, where the working fluid is an incompressible liquid, to arrange the exhaust ports 124, 122 so that they are exposed by the advancing vanes at the point of maximum volume of the fluid charge in the chambers. The positioning of the intake ports is critical to efficiency since it establishes the intake cutoff. To afford increased fluid exhaust capacity, additional exhaust port area may be provided such as by means of the auxiliary exhaust ports 126, 128 connected through branch passageways with the branch outlet passage 1 10, as shown in FIG. 3.

Where the rotary engine 20 is used as a gas compressor, or in other applications in which it would be ncessary to dissipate heat from the elements, a plurality of cooling fins 130 are provided around the outer periphery of secondary rotor 24. It will be seen that air cooling through the fins is assisted by the rotational movement of the fins with the secondary rotor.

FIG. 6 illustrates an embodiment of the invention providing removable and radially adjustable vanes 132. The vanes 132 are mounted within and project inwardly from lateral slots 134 formed in secondary rotor 24 at each vane position. Recessed seats 136 are formed in the outer surface of the secondary rotor on either side of the vane slots. Vane 132 is formed with a T-shaped head adapted to fit within the rotor seats 136. Suitable fastener means are provided to removably mount the vanes in position, and this fastener means may comprise the plurality of threaded studs 138 mounted into tapped holes in the secondary rotor and with lock nuts 140 turned onto the studs to lock the vanes in seated position. As required; one or more shims 142 may be provided to adjust the'radial position of each vane and thereby provide a means for adjusting the clearance of the inner vane edge and its associated seal 144 with respect to the hub 52 of the primary rotor. Y

FIG. 7 illustrates an embodiment of the invention providing a fluid valving arrangement characterized in having a positive valve action in which the design parameters may be selected so that the valve is opened for only a predetermined arc of rotation. The valving arrangement will be explained in relation to an inlet function, although it is understood that the arrangement also has application for an outlet function. In this embodiment a base support 146 mounts a stator element 148 which in turn rotatably supports a secondary rotor 150 through ball bearing assembly 152. A primary rotor is mounted for conjoint rotation with the secondary rotor within the stator'cavity according to the construction described'above for rotary engine 20. The inlet porting arrangement, is modified from that of engine 20 in that a relatively short length, axially extending inlet passage 154 is formed in rotor 150 and adapted to turn in registry with the open end of inlet conduit 156 leading from the desired fluid source'and with the end ofthe adjacent inlet passage 158 formed in stator 148. Inlet passage 158 extends through the stator where it opens into the leading portion of the adjacent chamber through an inlet port. lt'will be appreciated that the valving arrangement of this embodiment eliminates the movement of the vane seals over the inlet/outlet ports. A similarly constructed valving arrangement would be provided on the opposite side of the engine for valving the fluid charge'into the second chamber.

In operation, of the embodiment of FIG. 7 the pressurized inlet fluid, for example the gas under pressure, is directedinto inlet conduit 156. With'the rotor elements turning secondary rotor passage 154 moves into registry between inlet conduit 156 and stator passage 158 to direct a charge of gas through the aligned openings and into the expanding volume of the associated chamber. It will be seen that the rotor passage 1.54 turns in unison with its associated inlet port in the chamber and thus the charge is injected into the chamher only when the passage 154 moves into registry with inlet conduit 156. The volume and timing of the inlet charge may be adjusted according to particular requirements and specifications by appropriate sizing and positioning of the rotor passage 154 and/or inlet conduit 156. Thus, enlargement of the diameter of passage 154 functions to increase the exposure to the open end of inlet conduit 156 and thereby admit a greater charge volume into the chamber for one cycle. This valving arrangement finds application in, for example, a gas motor embodiment hereof so that the inlet circuit is open throughout a fraction of the rotational cycle for admitting a defined volume of pressurized gas, which then expands in the chambers to turn the rotors.

F IG. 8 illustrates. another embodiment of the invention providing a modified fluid valving arrangement operating responsive to relative movement between the primary rotor 156 and stator 158. In this embodiment the rotor 156 is mounted for rotation about the stator by suitable ball bearing assemblies 160. A secondary rotor 162 is mounted for rotation about the stator through ball bearing assembly 164 for conjoint rotation with primary rotor 156, and with projecting vanes being provided in accordance with the construction of rotary engine to produce expanding and contracting volumes within the cavity chambers. The valving arrangement will be explained in relation to aninlet function, although it is understood that the arrangement also has application for an outlet function. An inlet conduit 166 connects from a source of fluid into an inlet passage 168 formed in the stator and leading to a port 170 positioned at the mid-span of the stator axle about which primary rotor hub 172 revolves. An inlet passage 174 is formed within primary rotor 156 with an inlet end positioned to turn into registry with stator inlet port 170, together with an inlet port 176 opening into the leading portion of the associated chamber. A similar inlet valving construction, not shown, would be provided for the diametrically opposite chamber.

In operation of the embodiment of FIG. 8, the pressurized fluid, for example acompressed gas, is directed through inlet conduit 166 and into stator passage 168. Rotation. of primary rotor 156 moves the inlet end of rotor passage 174 into. registry with stator port 170 so that a charge of the fluid is admitted into the rotor passage where it issuesfrom inlet port 176 into the chamber. Where the charge is a compressed gasit will expand within the chamber and act against the associated vane to produce a driving torque for turning the rotor elements. The timing and volume of the inlet charge may be varied in accordance with particular specifications and requirements by a selected design positioning and diameter of stator port 170 and/or rotor passage 174. For example, an increase in port 170 diameter produces anincrease in the volume of the charge admitted into rotor passage 174 and the associated chambet for one cycle.

FIG. 9 illustrates generally at 178 another preferred rotary engine embodiment of the invention in which an output/inputdrive shaft 180 is keyed for rotation with third element primary rotor 182. The drive shaft is journalled for rotation within the annular cavity of a first element stator 184 by means of ball bearing assemblies 185. Stator 184 is anchored to an enclosing housing 186 which in turn is mounted by suitable means such as bolts to a base support 188. A second element or secondary rotor 190 of annular configuration is journalled for rotation about the stator by meansof ball bearing assemblies 192. The rotational axis 194 of the primary rotor and shaft is disposed at an oblique angle C with respect to the rotational axis 196 of the secondary'rotor in a manner similar to that explained above for rotary engine 20.

Secondary rotor element 190 is of annular configuration and may be constructed into sub-assemblies 198, 200 mounted together by suitable means such as bolts to facilitate assembly and disassembly.

Secondary rotor 190 carries partition means comprising a pair of diametrically opposed vanes 202, 204 which are mounted in suitable slots formed in the inner spherical surface 206 of this rotor with the vanes projecting radially inwardly into the annular stator cavity. While a pair of vanes are illustrated,it will be understood that the number of vanes could be greater than two with equal circumferential spacing, or only one vane could be provided, depending upon the desired number of volumes around the rotor.

Primary rotor 182 is formed in the shape of a disc with its outer rim defining a truncated section of a spherical surface for relative lateral sliding motion with respect to the inner surface 206 of the secondary rotor. The primary rotor is mounted'for rotation with shaft 180 by suitable means such as the key 208 secured within facing keyways machined in the shaft and rotor opening 210 through which the shaft projects. The shaft projects from either side of the primary rotor through a bore 212 extending through the stator. The outer ends of the shaft are rotatably mounted within the stator by suitable bearing means such as the illustrated roller thrust bearing assemblies 214, 216.

The angular disposition of the plane of rotation for primary rotor 182 within the stator cavity divides the same into two diametrically and axially opposed chambers through which the conjointly moving rotor elements carry the vanes to create the expanding and contracting volumes in a manner similar to that explained above for rotary engine 20. The stator sidewalls within the cavity are formed with diametrically opposed flat surfaces 218, 220 each defining annular sectors positioned in close-spaced relationship with the opposed rotating flat surface of a respective side of primary rotor 182. The remaining portions of the stator sidewalls are formed into diametrically opposed surfaces 222, 224 each defining truncated segments of a conical surface. The conical surface portions of the stator sidewalls provide close-spaced relative motion with respect to the radial edges of the vanes as they. are carried through the chambers.

Swivel seal means 226, 227. is provided to afford a swivel connection between the vanes and second and third elements to accommodate the relative swivel movement as the two rotor elements turn relative to the stator about their axes 194, 196. The swivel seal means comprise slotted cylinders 228, 230 of a construction similar to that provided for engine 20. These cylinders are seated within radially extending diametrically opposed bores formed in primary rotor 182 with respective slots of each cylinder adapted to slidably receive the corresponding vanes. As previously described, the vane movement throughout a complete cycle of rotation comprises a lateral sliding movement backand forth through the cylinder together with a swivel movement about radially. extending axes.

The vane edges are sealed with irespect to the stator sidewalls-and primary rotor by means of suitable U- shaped seal elements 232, 234, which may be segmented, disposed in slots formed along each of the vane side edges and inwardly projecting edges. The

. 12 vane'edge seals functibn to seal the chambers in the manner explained above in connection with the first embodiment. Additionally, labyrinth type seals 236, 238 are provided for sealing the peripheral end edges of stator 184 with respect to the inside corner edges of secondary rotor 190. Suitable annular seals, not shown,

similar to the seals 98, described in connection with rotary engine 20 may be provided to seal the outer spherical surface of primary rotor 182 with respect to the inner spherical surface 206 of secondary rotor 190. A pair of annular labyrinth type seals 240, 242 are provided radially inwardly of the vanes and between the facing surfaces of stator 184 and primary rotor 182. The seals 240, 242 complete the sealing of the chambers by preventing escape of fluid into the space between the shaft and stator central opening.

Inlet and outlet means are provided to introduce and discharge fluid and/or gasses into the expanding and contracting volumes of the chambers, depending upon the particular application of rotary engine 178. For example, where engine 178 comprises an internal combustion engine embodiment as illustrated in FIG. 10, the inlet meanscomprises an inlet conduit 244 connected with an inlet passage 246 formed in the stator and leading to an inlet portwhich opens into the leading portion of one stator chamber. The outlet means comprises a discharge conduit 248 connected with a discharge passage 250 formed in the stator and leading from a port which opens into the trailing portion of the other of the stator chambers. Suitable valve means of the type described hereafter in connection with FIGS. 1 1 18 is provided to transfer the charge from the trailing portion of the chamber communicating with the inlet means across through primary rotor 182 and into the leading portion of the opposite chamber. In an internal combustion embodiment of the engine of FIG. 9 suitable ignition means of the type shown in FIG. 10 is provided to ignite a compressed fuel/air charge in the leading portion of the lastmentioned chamber to initiate the combustion phase of the cycle and produce the driving torque for turning the rotor elements and drive shaft.

FIG. 10 is a schematic developmental view of a rotary engine 252 providing an internal combustion engine embodiment of the invention. Rotary engine 152 maybe adapted to embody the principles .of either of the above described rotary engines 20 or 178, i.e., an engine of the type in which the power shaft is connected for rotation with the secondary rotor as in engine 20, or of the type in which the shaft is connected for rotation with the primary rotor as in engine 178.

Internal combustion engines 252 comprises a stator 254 defining an internal cavity adapted to contain a primary rotor 256 and secondary rotor 258. The two rotor elements are mounted for conjoint rotation about oblique axes and are arranged to divide the stator cavity into diametrically and axially opposed chambers 260, 262 in the manner previously explained. A pair of diametrically opposed vanes 264, 266 are carried in swivel seal means 268, 270 which in turn are mounted within the primary rotor. Suitable sealing means 272, 274 is provided to seal the vane edges with respect to the sides of the stator cavity. ttator Inlet means is provided comprising an inlet conduit 276 connected with a passage 278 leading to an inlet port 280 which opens into the leading portion of chamber 262, with the direction of rotor element movement l3. being from top to bottom as viewed in FIG. 10. Inlet conduit 276 is connected with a suitable carburetor, where the inlet charge is a fuel/air mixture, or to a source of air .where a fuel injection arrangement, not shown, is provided. Outlet means is provided comprising a discharge conduit .282 connected with a passage 284 leading from discharge ports 286 which open into the trailing portion of chamber 260 for discharging the spent gasses therefrom. As a modification, the compressed charge may pass into a third combustion chamher where ignition occurs,as in a diesel preignition chamber, and the expanding gas then would be valved into the expanding chamber.

Suitable ignition means is provided to ignite the compressed and transferred charge in the leading portion of chamber 260. This ignition means comprises a pair of spark plugs 288, 290 mounted at diametrically opposed positions on secondary rotor 258 immediately adjacent a respective swivel seal and vane location with the electrodes adapted to communicate with the chambers. A suitable timing arrangementmot shown, is provided to energize each ignition plug asthe same is moved to a position relative to the stator as the compressed charge is transferred into the leading portion of chamber 260. Each plug thus fires one time for each revolution of the elements so that there are two combustion'phases or power pulses for each such revolution. 7

Valving means is provided to transfer the compressed charge from the trailing portion of chamber 262 across to the leading portion of opposite chamber 260 prior to the combustion phase. The valving means includes a pair of flow control valves illustrated schematically at 292, 294. Each of the flow valves is positioned adjacent a respective one of the vanes 264, 266 and is adapted to open communication between the chambers 260 and 262 when the rotary elements move to a predetermined positional relationship with respect to the stator. In the embodiment of FIG. 10 this charge transfer would occur through valve 292 when vane 264 is in the illustrated position with respect to the stator, i.e., so that the charge-which is compressed in'the contracting volume in chamber 262 ahead of vane movement is transferred across into the expanding volume of chambe 260 trailing vane movement.

The flow valves 292, 294 may comprise one-way flow control valves of the poppet or reed type construction which would be adapted to open responsive to a predetermined build-up of charge pressure. The flowvalves- 292, 294 may also comprise the valvingarrangements of FIGS. 11 through '18 which are actuated responsive to the particular positional relationships, depending upon the particular valving embodiment, assumed by the relative movement of the elements as they move through a given segment of the cycle of operation. It is understood that the following explanation of the operation of the flow valves for the internal combustion rotary engine 252 will have application to an engine of this type incorporating any one of these charge valving arrangements.

The flow valve 292 is typical, and it is understood that the following explanation has equal application to the construction and operation of valve 294. A flow passage 296 is formed on the side of primary rotor 256 with an outer opening communicating with chamber 262 ahead of the rotational sense of vane 264, and with an inner opening facing the cylinder of swivel seal means 268. Additionally, a flow passage 298 is formed on the opposite side of the primary rotor with an outer opening communicating with chamber 260 behind lished at the time that the two rotor elements move into a position relative to the stator where the transfer of the compressed charge is desired. When each flow valve 292, 294 is carried 189 from this position to the extreme opposite side, i.e., at the position for valve 294 shown in FIG. 10, the cylinder swivels to a position such that its associated transverse passage moves completely out of communication with the adjacent flow passages of the primary rotor.

The operation of internal combustion rotary engine 252 will be explained in relation to a suitable carburation arrangement for introducing a fuel/air charge into inlet conduit 276, although it is understood that the inlet charge could be air with suitable fuel injector means for the timed introduction of a precise charge of fuel intothe leading portion of chamber 260. Relative rotation of the two rotor elements with respect to the stator sweeps vane 266in the direction shown past inlet port 280 so that the expandin g volume of the leading portion of chamber 262 inducts the'charge from inlet conduit 276 into this chamber. This intake phase continues until a maximum volume of the charge is inducted. The following vane 264 then moves over and occludes intake port 280 to initiate the compression phase. Movement of this following vane creates the contracting volume in the trailing portion of chamber 262 and, at the same time, another intake charge will be inducted through inlet port 280 behind the movement of vane 264. Compression of the charge ahead of vane 264 continues with the cylinder of swivel seal 263 progressively'turning until transverse passage 300 is in registry with the rotor flow passages 296, 298. The

. compressed charge then flows from the trailing portion of chamber 262 through these alignedpassages and throughflow valve 292 into the leading portion of chamber 260. The ignition timing mechanism then energizes spark plug 288 which combusts the compressed charge with the expanding gasses applying torque forces against vane 264 for turning the rotors. This combustion-phase continues until vane 264 sweeps by and exposes outlet ports 286. The spent gasses exhaust through the outlet ports and discharge conduit 282, with the action of the following vane 266 serving to scavenge the waste gasses from chamber 260. At the same time that the leading face of vane 266 is scavenging to complete the exhaust phase, the trailing face of this vane is receiving the torque forces resulting from the next successive combustion phase in the leading portion of chamber 260. It is noted that because the two spark plugs turn with the rotors, the timing mechanism will function to energizethe spark plug 290 when the vane 266 moves to the position from that illustrated in FIG. 10. I

FIGS. 11 and 12 illustrate another embodiment of the invention providing a valving arrangement of the type adapted for transferring the compressed charge 

1. A rotary engine comprising a first element, a second element mounted for relative rotation with respect to said first element about a first axis, a third element mounted for relative rotation with respect to said first element about a second axis intersecting said first axis at a predetermined oblique angular relationship therewith, means forming an annular cavity concentric with said first axis and with said third element disposed in a plane extending diagonally across said cavity to define diametrically disposed chambers, partition means extending radially across said cavity, swivel means to interconnect said partition means for relative movement with respect to said third element whereby relative rotation of said first element with respect to said second and third elements creates expanding and contracting volumes within said chambers on either side of said partition means, inlet means to direct fluid into at least one of the expanding volumes, and outlet means to discharge fluid from at least one of the cotracting volumes.
 2. A rotary engine as in claim 1 in which said first element is formed with internal side walls defining a portion of said annular cavity, said third element is mounted within said cavity for conjoint rotation with said second element about said second axis, said partition means is mounted on said second element to project into said cavity, and said partition means is formed with side edges adapted for close-spaced relative motion with respect to at least a circular sector of respective first element side walls.
 3. An engine as in claim 2 in which the swivel means comprises cylinder means mounted on said third element for swivel movement about a longitudinal axis extending radially of said third element, said cylinder means including means forming radially extending slots for receiving said partition means in slidable sealing relationship therewith.
 4. An engine as in claim 2 in which diametrically opposed portions on opposed side walls of said first element define substantially flat surfaces in close-spaced relationship with an adjacent side of said third element, and with additional diametrically opposed portions of said walls defining truncated segments of a conical surface for providing said close-spaced relative motion with respect to said side edges of the partition means.
 5. An engine as in claim 2 in which said partition means comprises at least a pair of diametrically opposed vanes mounted on the inner surface of said second element and extending radially inwardly therefrom, and said swivel means includes means forming radially extending slot means seating respective vanes in slidable sealing relationship therewith and adapted to accommodate an arc of swivel motIon of said vanes with respect to said third element about radially extending axis during rotation of said second and third element with respect to said first element.
 6. An engine as in claim 5 in which said first and second axes for the respective second and third elements are disposed at an oblique angular relationship which is associated in a predetermined relationship between the axial width of said vanes and axial width of said cavity so that a respective radial side edge of a vane moves alternatively into slidable relationship with diametrically opposed segments of facing side walls of said first element followed by movement in axially spaced-apart relationship with additional diametrically opposed segments of said facing side walls.
 7. An engine as in claim 5 including means to selectively vary the radial inward extent of said vanes with respect to said second element.
 8. An engine as in claim 2 in which said first element comprises a fixed stator, said third element comprises a primary rotor, together with power shaft means constrained for rotation with said third element for delivering or receiving power to or from the rotating elements.
 9. An engine as in claim 8 in which said shaft means is co-axial with said second axis and extends through said stator, and said second element comprises an annular rotor journalled for rotation on said stator.
 10. An engine as in claim 2 in which said first element comprises a fixed stator, said third element comprises a primary rotor journalled for rotation about said stator, and said second element is journalled for rotation with respect to said stator and includes shaft means for delivering or receiving power to or from said second element.
 11. An engine as in claim 2 for use as a fluid pump or motor in which said cavity is formed into diametrically and axially opposed first and second chambers, said partition means comprises at least one vane means which moves through andseparates respective and separates into said expanding and contracting volumes, said inlet means includes conduit means to direct a supply of fluid into said chambers on the ends thereof corresponding to said expanding volumes, and said outlet means includes additional conduit means to discharge fluid from the ends of said chambers corresponding to said contracting volumes.
 12. An engine as in claim 11 which includes fluid valve means to control fluid flow through said inlet conduit means or through said additional conduit means.
 13. An engine as in claim 12 in which the valve means controls flow through said inlet conduit means, the inlet conduit means is formed partially in said stator with axially spaced conduit portions between which the second element moves and said valve means includes passage means formed in the second element to move into and out of fluid communication between said conduit portions.
 14. An engine as in claim 12 in which the inlet or additional conduit means is formed partially in said stator with a flow port, and said valve means includes passage means formed in the third element to move into and out of fluid communication between said port and chambers.
 15. An engine as in claim 11 for use as a fluid motor including means to direct fluid under pressure into said first conduit means whereby the reaction force resulting therefrom within said chambers causes relative rotation of said second and third elements with respect to said first element.
 16. An engine as in claim 11 for use as a fluid pump including power input means to impart relative rotation between said first element and said second and third elements whereby the contracting volumes of said chambers pressurize the fluid therein for discharge through said additional conduit means.
 17. An engine as in claim 11 in which said first element comprises a fixed stator, said third element is journalled for rotation with respect to said stator, said second element is journalled for rotation with respect to said stator and includes means to rotate said second element for pumping fluid under pressure through said outlet means or to deliver power responsive to pressurized fluid directed through said inlet means.
 18. An engine as in claim 17 wherein said inlet conduit means is formed in said stator and includes inlet ports opening into said chambers adjacent said expanding volumes thereof, and said outlet conduit means is formed in said stator and includes outlet ports opening into said chambers adjacent said contracting volumes thereof.
 19. An engine as in claim 2 for use as an internal combustion engine in which said cavity defines diametrically and axially opposed first and second chambers, said partition means includes at least two partitions which move through and separate the chambers into said expanding and contracting volumes, said inlet means includes conduit means to direct a charge of air or a combustible gas mixture into the expanding volume of the first chamber behind the movement of one of said partitions whereby the movement of the next succeeding partition through the first chamber compresses the charge into said contracting volume, valve means to direct the compressed charge from the first chamber into the expanding volume of said second chamber behind movement of a partition therethrough, means to combust the charge in the expanding volume of said second chamber whereby the pressure of the combusted charge causes relative rotational movement between said first element and said second and third elements, and said outlet means includes conduit means to exhaust the combusted charge from the contracting volume of said second chamber.
 20. An engine as in claim 19 in which said first element comprises a fixed stator, and said third element comprises a primary rotor including shaft means constrained for rotation with said primary rotor to delivery rotary power therefrom.
 21. An engine as in claim 20 in which said shaft means is coaxial with said second axis and extends through said stator, and said second element comprises an annular rotor journalled for rotation about said stator.
 22. An engine as in claim 19 in which said first element comprises a fixed stator, and said third element comprises a primary rotor journalled for rotation about said stator, said second element being journalled for rotation about said stator and including shaft means constrained for rotation with said second element to deliver rotary power therefrom.
 23. An engine as in claim 22 in which said inlet means includes inlet conduit means formed in said stator and having an inlet port opening into said first chamber adjacent the expanding volume thereof, and said outlet means includes outlet conduit means formed in said stator and having an outlet port opening into said second chamber adjacent the contracting volume thereof.
 24. An engine as in claim 19 in which said swivel means comprises cylinder means mounted in said third element for swivel movement about a longitudinal axis extending radially of said third element, said cylinder means including means defining radially extending slots for receiving said partitions whereby relative rotation of said first element with respect to said second and third elements causes said cylinder means to swivel about its longitudinal axis between extreme first and second positions, and said valve means includes channel means extending in fluid communication from the contracting volume of the first chamber to the expanding volume of the second chamber together with operating means to open and close communication through the channel means responsive to relative movement of the cylinder means.
 25. An engine as in claim 24 in which said channel means is formed partially through a side of said third element adjacent one of said partitions and including an inlet opening adapted to move into communication with the contracting volume of said first chamber and an outlet opening adapted to move into communication with the expanding volume of said second chamber, said channel means further beIng formed partially in said cylinder means and positioned to establish fluid communication between said channel means inlet and outlet openings responsive to swivel movement of said cylinder means when the latter moves relative to said first element in the region of the contracting volume and expanding volume of respective first and second chambers.
 26. An engine as in claim 24 in which said operating means is responsive to the relative position of one of said partitions with respect to the cylinder means, said channel means is formed partially in said one partition and includes an inlet opening adapted to move into communication with the contracting volume of said first chamber and an outlet opening adapted to move into communication with the expanding volume of said second chamber, and said channel means is formed partially in said cylinder means and establishes communication between said channel inlet and outlet openings responsive to relative sliding movement of the partition means with respect to said cylinder means when the latter moves into the region of the contracting and expanding volumes of respective first and second chambers.
 27. An engine as in claim 19 in which said valve means includes channel means formed partially in the second element, together with an inlet opening communicating with the contracting volume of said first chamber and an outlet opening communicating with the expanding volume of said second chamber, and means to open and close communication between said inlet and outlet openings responsive to said second element rotating to a predetermined angular position with respect to said first element.
 28. An engine as in claim 27 in which said means opening and closing communication between said inlet and outlet openings comprises a valve plate mounted for sliding movement on said second element between a first position opening said communication and a second position closing said communication, together with cam means to actuate said valve plate between said first and second positions responsive to relative rotation between said first and second elements.
 29. An engine as in claim 19 in which said valve means includes channel means formed partially in said stator and including inlet and outlet openings therein which lie in the region adjacent to respective contracting and expanding volumes of respective first and second chambers, said channel means further being formed partially in said third element adjacent one of said partitions and including first and second channels establishing fluid communication between respective inlet and outlet openings and respective contracting volumes of the first chamber and expanding volumes of the second chamber responsive to relative rotational movement of said third element with respect to said first element.
 30. An engine as in claim 1 in which said means forming the annular cavity includes axially spaced-apart side walls carried by said second element, and said third element is formed with annular side faces adapted to move into lines of tangential contact with diametrically opposed portions of said second element side walls.
 31. An engine as in claim 30 for use as a gas compressor in which said first element comprises a fixed stator and said inlet means includes means forming inlet ports through said second element side walls positioned with respect to said partition means on the side thereof lying behind the direction of rotation of said second and third elements with respect to said stator.
 32. An engine as in claim 30 in which said first element comprises a fixed stator, and said outlet means comprises exhaust passage means formed in said third element and having exhaust port means opening into said contracting volumes of the chambers and outlet port means, said outlet means further including additional exhaust passage means formed in said stator and having inlet and outlet opening means, said inlet opening means being positioned in registry with the path of movement of at least one of the third element exhaust passage outlet port means whereby relative rotation of the third element with respect to the stator controls the discharge of fluid from the chambers.
 33. A rotary engine as in claim 30 in which said partition means comprises at least one vane secured to said second element, the outer edge of said vane being sealed with respect to the outer peripheral wall of said second element, and the radial side edges of said vane being sealed with respect to said second element side walls.
 34. A rotary engine as in claim 1 in which said swivel means comprises means forming a swivel cylinder seated in said third element for back and forth swivel movement about a radially extending, longitudinal axis, means forming a slot in said cylinder means extending laterally across said annular cavity with said partition means being mounted for lateral slidable and sealable back and forth movement through said slot during said relative rotation of said elements.
 35. A rotary engine as in claim 34 in which said third element is formed with a central hub portion with means forming a circular recess in said hub portion about the lower margin of said swivel means with the base of said recess having a spherical surface, and means forming a circular shoulder at the lower margin of said swivel cylinder, said shoulder being formed with a spherical shell configuration and being seated in said hub recess for relative sliding and pivotal movement therewith during said relative rotation of said elements.
 36. A rotary engine as in claim 34 in which said partition means is formed with an arcuate inner tip, a cylindrical recess is formed in said third element at the radially inner base of said swivel cylinder, with the base of said swivel cylinder seated in said recess, and an arcuate surface is formed in said cylinder base along the lower margin of said slot for slidable sealing contact with the tip of said partition means.
 37. A rotary engine as in claim 34 which includes pressure relief chamber means formed at either of the interfaces between a side of said swivel cylinder and an adjacent portion of said third element or between the slot of said swivel cylinder and an adjacent surface of said partition means, and means to communicate fluid under pressure into said chamber means to unload the normal forces acting at said interfaces during said relative rotation of said elements.
 38. A rotary engine as in claim 37 in which said means communicating fluid comprises passageway means formed in said third element and having inlet means communicating with the contracting volumes of said chambers and outlet means communicating with said pressure relief chamber means.
 39. A rotary engine as in claim 30 which includes means to form a fluid-tight seal between the volumes of said chambers on either side of said lines of tangential contact between the second and third elements, said last mentioned means comprising a plurality of radially extending, circumferentially spaced-apart sealing elements, and means to seat said sealing elements with said second element for limited lateral displacement therewith whereby fluid under pressure within said contracting volumes acts upon said sealing elements and urges the same into sealing relationship with the opposing side faces of said third element along said lines of tangential contact.
 40. A rotary engine as in claim 39 in which said sealing elements each comprise elongate pins formed to taper with a smaller diameter at their radially inward ends, and said seating means comprises a plurality of radially extending, circumferentially spaced-apart grooves formed in said second element side walls together with a plurality of radially extending grooves formed in said third element side faces in registry with respective second element grooves, whereby said fluid under pressure urges said pins to occlude the clearance between two facing grooves between the second and third elements in the region of said lines of contact.
 41. A rotary engine as in claim 39 in which said sealing elements comprise elongate inserts each formed with T-shaped cross-sectional configurations, and said seating means comprises a plurality of radially extending, circumferentially spaced-apart T-shaped slots formed along the inner surface of said second element side walls, each of said inserts being mounted for lateral displacement in a respective slot and with a clearance being provided between said inserts and slot side walls whereby pressurized fluid within the contracting volumes of said chambers communicates into said slots and urges the sealing inserts contained therein toward the third element side faces for sealing the volumes on either side of said lines of tangential contact.
 42. A rotary engine as in claim 30 which includes means to form a fluid-tight seal between the chamber volumes on either side of said lines of tangential contact comprising means forming a plurality of radially extending, alternating lobes and recesses together forming a convoluted surface about the inner surface of said second element side walls, and means forming a plurality of radially extending, alternating lobes and recesses together forming a convoluted surface on the third element side faces, said third element lobes and recesses being adapted to move into seated relationship with opposed second element recesses and lobes in the region of said lines of tangential contact to form said fluid-tight seal.
 43. A rotary engine as in claim 30 in which said partition means comprises a plurality of circumferentially spaced-apart vanes extending across the cavity of said second element, said inlet means include means forming inlet ports in said second element side walls positioned on the sides of said vanes lying in the direction of relative advance of said lines of tangential contact between said second and third elements, and said outlet means includes means forming outlet ports through said second element side walls and positioned on the sides of said vanes lying in the direction behind the advance of said lines of tangential contact.
 44. A rotary engine as in claim 43 which includes one-way flow control means to direct inlet fluid through said inlet ports into the expanding volumes of the chambers associated therewith and additional one-way flow control means to direct exhaust fluid through said outlet ports from the contracting volumes of the chambers associated therewith.
 45. A rotary engine as in claim 1 in which said second element comprises a fixed stator, and said third element comprises a disc mounted for precessional-type motion within said annular cavity responsive to said relative rotation of said elements, said precessional-type motion causing the advance of diametrically opposed lines of tangential contact between the disc and second element in the direction of rotation of said first element to create said expanding and contracting volumes.
 46. A rotary engine as in claim 45 in which said partition means comprises at least one vane mounted to said second element, said inlet means includes means forming inlet ports through said second element and positioned on a side of said vane lying in the direction of advance of said lines of tangential contact, and said outlet means includes means forming outlet ports through said second element lying on a side of said vane behind the direction of advance of said lines of tangential contact.
 47. A rotary engine as in claim 46 for use as a gas compressor which includes one-way flow control means to direct exhaust gases through said outlet ports from the contracting volumes of the chambers associated therewith.
 48. A rotary engine as in claim 45 which includes bearing means mounting said first element for relative rotation with respect to said third element about said second axis, said bearing means supporting load forces having axial components. 